CN87103586A - crushing equipment - Google Patents

Abstract

A breaker for breaking rock-like material has breaking means driven to oscillate towards and away from each other and supported at their proximal ends on a frame. Most of this movement is in the horizontal direction, so it is essentially a balanced device.

Description

Crushing equipment

The present invention relates to a crushing device.

The apparatus of the present invention is useful for crushing rocks, as will be described in detail herein. It is also useful for crushing other materials (e.g., glass, ore, bricks, granular materials).

Currently, there are several types of equipment used for crushing: ball mills, rod mills, hammer mills, and jaw crushers. However, for "precision" crushing, that is, crushing the material to obtain particles within a strict size range with a low level of fines, jaw crushers are generally used. The most common jaw crusher uses a hammer-anvil action—a movable jaw swings against a fixed jaw. The position of the fixed jaw can be adjusted to change the minimum gap between the jaws. This type of crusher is very effective, but it is quite wasteful because a large part of the force of the movable jaw is absorbed by the fixed jaw and not used to crush the material. Therefore, this device requires a heavy base to withstand the uneven load imposed on the device by the impact of the fixed jaw. This type of jaw crusher is shown and described in Australian Patent No. 227301 and U.S. Patents Nos. 2,326,316 and 4,124,170.

Several existing patents attempt to address this problem by using a crusher design in which both jaws are driven. For example, U.S. Patent No. 427,441 discloses a crusher with two vertically mounted jaws, spaced apart, and each jaw swinging near its base. The jaws are driven near their upper ends so that they swing simultaneously in the same direction, causing the material squeezed between the jaws to undergo a grinding and crushing action due to the relative motion of the crushing surfaces, one upward and the other downward. A major disadvantage of this design is that the material between the jaws is ground rather than impacted by the jaws, significantly reducing the impact force that the jaws can exert. Furthermore, a significant portion of the power required to drive the jaws is wasted on moving the jaw plates up and down rather than on the jaws striking the material to be crushed.

U.S. Patent No. 472,367 discloses a crusher comprising a pair of opposing jaws whose lower ends roll on supporting rollers. The jaws are driven eccentrically toward and away from each other, so that one jaw always moves faster than the other, and the relative surfaces of the jaws are constantly changing. However, this eccentric motion means that the two jaws do not impact the material being crushed equally. Furthermore, this design has the disadvantage that the roller mounting of the jaws constrains the lower ends of the jaws to remain in the same position, preventing them from swinging freely in a parallelogram motion. Consequently, side loads on the jaws are transferred directly to the crusher's supporting housing rather than being absorbed by the jaws themselves.

The crusher disclosed in U.S. Patent No. 3,079,096 shares many structural similarities with U.S. Patent No. 472,367. Its pair of jaws are mounted at their lower ends for vibration, with the lower end of each jaw supported and restrained by an elastic support. During use, the jaws vibrate toward and away from each other, but cannot freely swing to form a parallelogram. Therefore, this structure also suffers from the drawbacks described in U.S. Patent No. 472,367.

In an effort to overcome the above-mentioned disadvantages, the applicant designed a crusher, which became New Zealand Patent No. 196191, having a pair of opposing, pivotally mounted crushing jaws that are free to swing from side to side in a parallelogram pattern, thus preventing the transmission of significant reaction forces to the support housing. The jaws are simultaneously driven toward and away from each other by a suitable drive mechanism located near the free ends of the jaws. While this arrangement has been found to be highly satisfactory in many applications, it has been found to be somewhat inadequate in certain applications (particularly when crushing gravel approaching the maximum size acceptable for the crusher). In particular, gravel of maximum or near-maximum size requires more uniform crushing along the entire length of the jaws. Furthermore, moist material tends to become lodged between the jaws and is difficult to remove.

An object of the present invention is to provide a crusher which overcomes the above-mentioned disadvantages of prior art crushers and, in particular, provides a crusher which has all the advantages of the crusher of New Zealand Patent No. 196191 and which has the additional advantage that the overall crushing capacity of the crusher is improved by enabling the crusher to crush over the full length of each jaw and by enabling the jaws to move in such a manner as to remove material which becomes lodged between the jaws.

The present invention provides a crusher comprising a pair of opposing crushing jaws, each jaw being swingably mounted on a supporting device to swing toward and away from each other; a pivot support of each jaw being adjacent to one end of the jaw, the one ends of the two jaws being arranged relative to each other, and the other ends of the two jaws being also arranged relative to each other; a first drive device being used to drive the two jaws to swing toward and away from each other simultaneously, and also to cause the two jaws to swing in the same direction simultaneously; and a second drive device being used to drive the one end of at least one jaw toward and away from the one end of the other jaw.

The jaws are preferably arranged so as to form facing walls of a downwardly converging hopper.

The one end of the two jaws can be placed near the top of the crusher, while the other end can be placed near the crusher bottom. The other end of the two jaws can also be placed near the top of the crusher while the one end can be placed near the crusher bottom.

The first drive means may comprise a unified drive means, or two separate drive means, one connected to each jaw.

One or both of the ends of the two jaws may be driven, and if both are driven, the second drive means may be a unified drive means or two independent drive means.

The first and second drive means may be independent or synchronized with each other.

By way of example, preferred embodiments of the present invention will be described with reference to the accompanying drawings, in which

FIG1 is an end view of the apparatus of the present invention,

Figure 2 is a side view of the device in Figure 1 with some of the frame components removed.

FIG3 is a cross-sectional view of the III-III section in FIG2 ,

FIG4 is a partial end view of FIG3, and

FIG5 is a cross-sectional view taken along the V-V section in FIG2 ,

Referring to the accompanying drawings, a rock crushing apparatus includes a lifting frame 10 having a top 11 and legs 12. Two pairs of crushing jaw pivot bearings 13 and 14 are mounted on the frame top 11. These two pairs of pivot bearings 13 and 14 face each other across the table 11. Two jaws 15 and 16 face each other. Each jaw 15 and 16 has a horizontal shaft 17 and 17a extending from each side of its upper end. The ends of each shaft 17 and 17a are pivotally fixed to the pivot bearings 13 and 14. Thus, the crusher jaws 15 and 16 are suspended from the table 11, facing each other.

The shaft 17a connected to the jaw 16 is also supported on a pair of eccentric bearings 40 which are connected in a known manner to the rear adjacent portion of the jaw 16 (Figure 5).

A pulley 41 is mounted on one end of shaft 17a and when the pulley is driven (as will be described below), shaft 17a rotates within eccentric bearing 40 causing jaw 16 to move eccentrically towards and away from jaw 15 near the upper ends of the jaws.

Another possible configuration (not shown) is to mount shaft 17 on an eccentric bearing instead of shaft 17a, or to mount both shafts eccentrically, so that one or both jaws 15 and 16 can be driven eccentrically, moving toward and away from each other near their upper ends. Alternatively, eccentric bearings may be omitted, and one or both shafts 17 and 17a may be eccentric to provide the desired eccentric motion at the upper ends of jaws 15 and/or 16.

The inner surface of the crusher jaw is preferably protected by a wear block 18, and its working surface can be provided with a plurality of ribs 19. The height of the ribs can be reduced towards one end. The inner crushing surface of the wear block 18 can be inlaid with carbide steel to reduce wear.

The wear-resistant block 18 can be fixed on 15, 16 by clamping, screwing or other methods, and can be turned over.

Jaws 15 and 16 are wider at the top than at the bottom and have two vertical end walls 20 and 21 welded to them, one at the end edge of each jaw. The free end of each end wall 20 and 21 abuts the adjacent end edge of the other jaw 15 and 16. Thus, jaw 15 moves with end wall 20, while jaw 16 moves with end wall 21. This arrangement creates a V-shaped hopper for the end walls and jaws. When the crusher is in operation, material to be crushed is loaded into the top of the hopper, falls through the crusher under the influence of gravity, and leaves the bottom of the crusher in a crushed state.

The end walls 20, 21 could be welded to opposite ends of one jaw 15, 16 with a small gap near the end of the other jaw 16, 15, but such an arrangement would destroy the balance and symmetry of the above arrangement.

The lower ends of the two jaws 15 and 16 are connected by a reciprocating mechanism, which causes the two crushing jaws to swing simultaneously about their pivot bearings 13 and 14. The reciprocating mechanism causes the two jaws to converge and separate simultaneously; each jaw moves with equal force. The reciprocating motion is provided by an eccentric 22 on a drive shaft 23. The drive shaft is horizontally mounted on two bearings 24 fixed to the outer surface of the lower end of jaw 15. The bearings extend beyond the width of the drive shaft 23. Two connecting rods 26 are mounted on the eccentric 22. The other ends of the connecting rods 26 are mounted on similar eccentric journals 27 on a transverse shaft 28. The transverse shaft is horizontally mounted on a bearing 29 fixed to the lower end of the other jaw 16, parallel to the drive shaft 23 on jaw 15.

A V-belt drive pulley 30 is fixed to the end of the drive shaft 23, and this pulley 30 is driven in a known manner by an electric motor (not shown). When the pulley 30 is driven, it rotates the drive shaft 23, so that the eccentric journal on the shaft 23 causes the jaw 15 to swing toward and away from the jaw 16.

Simultaneously, connecting rod 26 reciprocates due to the effect of shaft 23 and causes jaw 16 to swing toward and away from jaw 15. Connecting rod 26 and shaft 23 are designed to cause two jaws 15 and 16 to move away from and toward each other simultaneously, and each jaw moves at the same speed.

Pulley 41 may be driven by pulley 30 or may be driven independently.

During normal operation, the connecting rod 26 does not move relative to the eccentric journal 27, but is clamped to the shaft 28 by a clamp fastened to the connecting rod 26 and can be loosened from the shaft 28 by means of a screw 32. When the shaft 28 is loosened, it can partially rotate within the connecting rod 26, allowing the eccentric journal 27 to adjust the wheelbase of the shafts 23 and 28, thereby changing the gap between the lower ends of the two jaws 15 and 16. The clamp 31 can then be tightened again.

The distance between the upper ends of the jaws 15, 16 can also be varied independently of the lower ends of the jaws, for example by removing the bolts of the bearings 13, 14 from the table 11 and repositioning them using different bolt holes (not shown) in the table 11.

If the eccentric journal 27 is not used, the distance between the bottoms of the two jaws 15, 16 can also be changed by a connecting rod of adjustable length, for example in the form of a tensioner with forward and reverse threads.

In some cases, the illustrated arrangement may be reversed, with the hopper still tapering downwardly, the upper ends of the jaws 15, 16 reciprocating, while the lower ends of the jaws are swingably mounted on the frame, one or both of the lower ends being eccentrically driven.

A key feature of the present invention is that the jaws 15 and 16 are capable of oscillating in a parallelogram motion about pivot bearings 13 and 14, rather than being fixed to the crusher frame. To achieve this, the drive shaft 23, pulley 30, and connecting rod 26 all oscillate with the jaws. Because the drive belt (not shown) running from the motor to pulley 30 is flexible, it does not restrict the jaws' motion. The simultaneous parallelogram-like oscillation of the jaws 15 and 16 prevents significant reaction forces from being applied to the crusher frame. Therefore, during crusher operation, the majority of the force applied by each jaw is transferred to the material being crushed, rather than to the opposing jaw. Significant force is transferred to the crusher frame, and this force is transferred solely through bearings 13 and 14. Consequently, (ignoring the eccentric drive at the upper ends of the jaws 15 and 16), the vertical motion of the center of gravity of each jaw assembly is minimal compared to its horizontal motion. Consequently, significant vertical vibration forces are transmitted to the frame 10, while horizontal forces are largely balanced and offset, significantly improving crusher efficiency. However, the eccentric drive of the upper ends of jaws 15 and/or 16 causes a greater component of vertical movement of the jaws - this is beneficial for clearing any material that becomes lodged between the jaws, as the downward movement of the eccentrically driven jaws helps to break up and clear any lodged material.

When the illustrated embodiment of the invention is in use, material to be crushed is poured into the top of the crusher (e.g., from a feed hopper). The lower ends of the two jaws 15 and 16 simultaneously swing toward and away from each other, and the upper end of jaw 15 also moves eccentrically toward and away from the upper end of jaw 16 (or, if both jaws are eccentrically driven, the jaws move toward and away from each other at their upper ends).

The extent of movement of the eccentric drive end of the or each jaw can be adjusted by adjusting the orientation of the eccentric bearing 40.

The eccentric movement of the upper end of the jaw or each jaw pre-crushes large gravels, thus solving the problem of large gravels (close to the maximum size that the crusher can accept) being squeezed out of the crusher when the lower edges of the two jaws move towards each other. The additional crushing caused by the eccentric movement of the upper end of the jaw or each jaw also helps to improve the overall crushing efficiency of the crusher. As discussed above, the eccentric movement of the upper end of the jaw or each jaw also helps to eliminate material stuck between the two jaws.

While it is desirable for the jaws 15, 16 to oscillate in a parallelogram motion (for reasons previously discussed), it may be desirable to dampen this oscillation somewhat. If this is desired, the jaws 15, 16 may be biased toward the center of the frame by a spring mechanism such as an elastomeric bushing 33, secured to a spacer 34 screwed to the leg 12. The inner core of the bushing is secured to a torsion arm 35, which is connected to the jaw 16 by a pivoting link. This biasing mechanism does not prevent the jaws from oscillating in a parallelogram manner, but rather dampens this oscillation and helps to urge the jaws toward the center.

The above-described crusher can be modified in many ways. First, the drives for the upper and lower ends of the two jaws 15 and 16 can be replaced by any other suitable drive. For example, the eccentric shaft 23 can be replaced by a straight shaft journaled in an eccentric bearing, while the straight shaft 17 and the eccentric bearing 40 can also be replaced by an eccentric shaft.

Secondly, the upper and lower ends of each jaw can be driven independently instead of linked; and the non-swinging end of each jaw can also be driven independently by a suitable synchronous drive device.

Thirdly, by using a chain sprocket drive, a gear drive or a toothed belt drive, the eccentric drive of the or each oscillating end of the jaw can be synchronized with the drive of the non-oscillating end of each jaw.

Claims (27)

1. A crusher comprising a pair of opposing crushing jaws, wherein each jaw is swingably mounted on a support device so as to swing toward and away from the other jaw; a pivot support of each jaw is adjacent one end of the jaw, the one ends of the jaws being disposed opposite each other, and the other ends of the jaws being disposed opposite each other; a first drive device is configured to drive the jaws to swing simultaneously toward and away from each other, and to cause both jaws to swing simultaneously in the same direction; and a second drive device is configured to drive the one end of at least one jaw toward and away from the one end of the other jaw. 2. A crusher comprising a pair of opposing crushing jaws, characterized in that each jaw is swingably mounted on a support device so as to swing toward and away from the other jaw; a pivot support of each jaw is adjacent to one end of the jaw, the one end of the jaw is arranged opposite to each other, and the other end of the jaw is also arranged opposite to each other; a first drive device is used to drive the jaws to swing simultaneously toward and away from each other, and at the same time, the two jaws can swing in the same direction at the same time; a second drive device is used to drive the one end of at least one jaw toward and away from the one end of the other jaw; the above-mentioned first drive device includes a drive shaft rotatably mounted on one of the above-mentioned jaws, the drive shaft forming an eccentric portion at each end thereof; a first connecting rod swings around one of the eccentric portions at one end and is supported on the shaft of the other jaw at the other end; a second connecting rod swings around the other eccentric portion at one end and is supported on the shaft of the other jaw at the other end; the above-mentioned two connecting rods both swing around the drive shaft and are supported on the shaft of the other jaw at a position away from the pivot support of the jaw. 3. The crusher according to claim 2, further comprising means for adjusting the minimum gap between the other ends of the two jaws when the two jaws swing toward each other. 4. A crusher as claimed in claim 3, characterized in that said means for adjusting said minimum gap comprises another shaft supported on said other jaw parallel to the drive shaft, said other shaft having another eccentric portion, said other end of the connecting rod being rotatable on and clamped to said other eccentric portion, whereby the distance between said pivot axes can be adjusted by rotation of the portion of said other shaft in said connecting rod. 5. A crusher as claimed in claim 2 or claim 4, characterised in that the said second drive means comprises a further drive shaft rotatably mounted on the driven jaw or each driven jaw adjacent its pivot support, the shaft being mounted in an eccentric bearing on the or each said jaw so that rotation of the shaft causes eccentric movement of the jaw towards and away from the other jaw. 6. A crusher as claimed in claim 5, characterised in that said eccentric bearing is adjustable relative to said further drive shaft so as to adjust the amount of movement of the or each jaw towards and away from said other jaw. 7. A crusher as claimed in claim 1 or claim 2, characterised in that the jaws are arranged to form facing walls of a downwardly converging charging hopper. 8. A crusher as claimed in claim 7, further comprising two end walls facing each other and extending from one jaw to the opposite jaw, one end of the jaw being provided with an end wall. 9. A crusher according to claim 8, wherein one end wall is firmly fixed to one end edge of one jaw and projects outwardly to pass over the opposite end edge of the other jaw with a small gap, and the other end wall is firmly fixed to one end edge of the other jaw and projects outwardly to pass over the opposite end edge of the one jaw with a small gap. 10. A crusher as claimed in claim 1 or claim 2, characterised in that the jaws have opposed working surfaces against which the material passing through the crusher is pressed to crush the material, the working surfaces being formed of removable and replaceable wear blocks. 11. A crusher as claimed in claim 10, wherein at least one of the working surfaces is formed with a plurality of parallel grooves extending toward the outlet of the crushed material. 12. A crusher as claimed in claim 11, wherein the depth of the groove gradually decreases from one end to the other end of the groove. 13. A crusher as claimed in claim 1 or claim 2, characterised in that said first and second drive means are synchronised with each other. 14. A crusher as claimed in claim 1 or claim 2, wherein said one ends of said two jaws are disposed near the top of the crusher and said other ends of said two jaws are disposed near the bottom of the crusher. 15. A crusher as claimed in claim 1 or claim 2, wherein the other ends of the two jaws are disposed near the top of the crusher, and the one ends of the two jaws are disposed near the bottom of the crusher. 16. A crusher as claimed in claim 1 or claim 2, wherein the pivot support of one jaw is movable towards and away from the pivot support of the other jaw. 17. A crusher as claimed in claim 1 or claim 2, characterised in that the jaws are resiliently biased towards a central working position. 18. A crusher as claimed in claim 1 or claim 2, wherein said one end of each jaw is drivable towards and away from said one end of the other jaw. 19. A crusher as claimed in claim 18, characterised in that said second drive means comprises a unified drive means for driving both jaws. 20. A crusher as claimed in claim 18, wherein said second drive means comprises two independent drive means, one connected to each jaw. 21. A crusher as claimed in claim 1 or claim 13, characterised in that said first drive means comprises two independent drive means, one connected to each jaw. 22. A crusher as claimed in claim 1 or claim 13, wherein said first drive means comprises a unified drive means for driving both jaws. 23. A crusher as claimed in claim 22, characterized in that said first driving means comprises a drive shaft rotatably mounted on said one jaw, an eccentric portion formed on the drive shaft, a connecting rod having one end pivotally pivoted about the eccentric portion and the other end supported on the shaft of the other jaw, the connecting rod pivoting about the drive shaft and supported on the shaft of the other jaw at a position separated from a pivot support of the other jaw. 24. The crusher according to claim 1, further comprising means for adjusting the minimum gap between said other ends of said two jaws when said two jaws swing toward each other. 25. The crusher according to claim 23, further comprising means for adjusting the minimum gap between said other ends of said two jaws when said two jaws swing toward each other, said adjusting means comprising means for adjusting the distance between said pivots at the ends of the connecting rods. 26. A crusher as claimed in claim 1 or claim 23, characterised in that said second drive means comprises a further drive shaft rotatably mounted on the driven jaw or each driven jaw adjacent its drive support, said shaft being mounted in an eccentric bearing on the or each said jaw so that rotation of said shaft causes eccentric movement of said jaw towards and away from said other jaw. 27. A crusher as claimed in claim 26, characterised in that said eccentric bearing is adjustable relative to said further drive shaft to adjust the amount of movement of the or each said jaw towards and away from said further jaw.

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